Speed transmission mechanism



Jan; 21, 1936. A. VINCENZONE 8,5

SPEED TRANSMISS ION MECHANISM Filed March 28, 1954 Sheets-Sheet l v INVENTOR 13/ I 191mm fiizcmzwzz' ATTORNEYS Jan, 21, 1936. WNCENZONI 7 2,028,577

SPEED TRANSMISSION mcmmxsm Fild March 28, 1934 s Sheets-Sheet 2 INVENTOR fill/am Ema/1201a afl- ATTORNEYS Jan. 21, 1936. fl cE zom 2,028,577

SPEED TRANSMISSION ME HANISM Filed March 28, 1934 '4 6 Sheets-Shet 3 v ,8 INVENTOR flfi gg'a i inrmzanz W [5/4 P V ATTORNEYS Jan. 2l, 1936. A. VINCENZQNI' SPEED TRANSMISSION MECHANISM Filed March 28, 1934 6 Sheets-Sheet 4- INYENTOR.

1 fllimm finrrzzzam ATTORN EYS Ja 21, 1936. A. VINCENZONI I 2,028,577 I SPEED TRANSMISSION MECHANISM Filed March 28, 1934 6 SheetfS-Sheet 5 INVENTOR v fllvam7191091120111 BY ATTORN EYS Jan. 21, 1936. A. VlNCENZONi SPEED TRANSMISSION MECHANISM Filed March 28, 1934 6 Sheets-Sheet 6 mpgu Patented Jan. 21. 1936 Application 4 Claims.

This invention relates to speed transmission mechanism. Among the objects of the invention is to provide a-mechanism which may be adiusted during its operation to vary the ratio of 6 angular velocities between rotary driving and driven members.

Another object of the invention is to provide a variable speed transmission mechanism which is continuously operative as a power transmit- 10 ting connection between a driving member and a driven member so that there is always provided a direct connection between the two members by which it is possible to vary the ratio of speed transmission and which automatically permits the overrunning-oi. the driving .member by the driven member.

Other objects involving novel constructions and combinations of parts will appear in the appended claims and in the specification which sets forth a. preferred embodiment of the invention.

The invention may be fully understood from the detailed description and drawings, in which Fig. 1 is a side elevation of a variable speed trans mission attached to a bicycle and embodying the principle of the invention.

Fig. 2 is a side elevation of the mechanism illustrated in Fig. 1, with the driving and driven members displaced from each other and in such position as to correspond to a gearing reduction.

Fig. 3 is a detail of a cam as seen from the .rear of Fig, 2.

Fig. 4 is a'sectional view takenon line l-@ of Fig. 1'.

Fig. 5 is a view taken from the rear of Fig. l with parts broken away.

Fig. 6 is a detail on line as of Fig. 5.

Fig. 7 is a schematic showing of a modified form of the variable speed mechanism as used herein for explaining the principle of the vention. Fig. 8 illustrates principal parts of a modifica tion of the variable speed transmission meohanism.

Fig; 9 is a section on line il--9 of Fig. 8.

Fig. 101s a-detail illustrating another mode of applying the invention.

Fig. 11 is still another modification of the variable speed transmission mechanism.

Fig. 12 is a section on line ii2 of Fig. 11. Fig. 13 is still another modification of the variable speed mechanism.

Fig. 14 is a section on line ifi-M of Fig. 13. Fig. 15 is a section of a detail taken on line IS-id of Fig. 13.

March as, 1934, Serial No. 717,691

'In Italy June 3,1933

" Fig. 16 is a front elevation on line I 6-46 of Fig.

Fig. 1'7 is a front elevation of the modification illustrated in Fig. 7, showing details 01! the variable cam. I

Fig. 18 is a side view of the variable illustrated in Fig. 1'7.

while the principleof the invention may be utilized in diflerent forms and for different uses; of which I have illustrated several by way of example, I have chosen to describe the same as con- 'structed for use upon a bicycle because 0! its general adaptability to such use. The invention provides for obtaining various ratios of speed transmission without dependence upon such speed transmission mechanism as requires disconnection between the driving and driven members.

, In its simplest form the invention consists of a pair oi rotatable shafts, one carrying a driv ing member and one carrying a driven member, which may 'be shifted in respect to each other from a position of eccentricity through a position of concentricity to an opposite position of eccentricity, and connecting means for transmitting motion from the driving member to the driven member. The connecting means include arms pivoted upon one oi the members in such a manher that they may be engaged by the other memher for a portion of the angular travel of the sec- 0nd member, the arms being so mounted as to continually rock in respect to both members whenever the members are in eccentric positions relative to each other. The relation of the arms to each other is such that they successively come into operation to transmit motion from one memher to the other member, whereby there is ah ways a direct connection between the two members, and this is so irrespective oi any change eccentricity of the two members while motion is being transmitted through the mechanism. Changes in eccentricity produce changes in ratio of speed transmission without'discontinuance of a direct driving connection.

it will be apparent from the description which iclicwsthat with suitable changes the functions of the driving and driven members may be reversed in respect to each other, and that the invention is susceptible toother variations owing to the fact that the lineal displacement of the driving and driven members and their respective shafts is relative in character.

The variable speed transmission mechanism illustrated in Fig. 1 includes a driving member it, a driven member I! and six connecting ele ments ii. The connecting elements are in the form of arms pivotally mounted on pivots l3 equi-spaced from one another upon the driven member The ends ll of the arms I 2 are providedwithrockers |5 carried by pins IS. The ends l4 may be considered as the free or floating ends of the arms l2 because they move in respect to the driving member when they are not connected to the driving member for driving the driven member.

Each rocker I5 is urged to rotate about its associated pin IS in a counter-clockwise direction (Fig. 1), by a spring I1. Each rocker l5 carries at its-extremity a dog l8 which is so proportioned as to fit within a 'channel'in the driving member which consists of two'grooves l9 (Fig. 4)

facing one another. The dog protrudes. lateral-q ly so as to enable simultaneous engagement with the two grooves l9 and each protrusion is so shaped as to cause engagement with opposite surfaces 20, 2| of each groove l9 when its rocker is rocked about its pivot in a counter-clockwise direction! The position of engagement ,of a dog l8 with the opposite surfaces 20, 2|, is illustrated in Fig. l and by the uppermost dog in Fig. 2, and different positions of the rockers, with the dogs out of engagement with the opposite surfaces 20, 2|, are illustrated by the lowermost rockers shown in Fig. 2. In the latter positions the dogs have been rotated clockwise about their pivots I6- againstthe' action of springs I1 and this is pos sible because the relative speeds of the driving member and driven member are such, at the particular positions, that the rockers and connecting arms are overrunning or oving at a greater velocity than the adjacent portions of the driving member. This action takes place during the periods of non-locking engagement of the dogs when thedriving member and driven member are in eccentric positions. Further explanation of the action of the connecting arms and engaging dogs will be given hereinafter in conjunction with the schematic showing of a similarly acting construction (Fig. 7).

Having reference to Fig. 1, 23 is the usual driving shaft which is employed on a bicycle and. to which the pedal arms 24 are connected This shaft is journalled in a hub 25, Fig. 4, and has connected thereto the driving member ID. The driving member generally designated as M may be made up as shown in Fig. 4 to include a pair of disks rigidly connected together and each carrying a circular groove l9. in As shown in Fig. 2 (and in Fig. 11) the dogs which'engage in'locking relation with the opposite and concentric surfaces and 2| of each groove |9 during periods of .power transmission between the driving and driven members are of an oval or elliptical shape and so proportioned as to allow free and non-locking relation with surfaces 20 and 2| when the dogs are rocked in one direction, and locked or engaging relation with surfaces 20 and 2| when the dogs are rocked in the opposite direction. As illustrated in Fig. 2, surface 2| is slightly fluted to increase the frictional contact with the dog but such marking is optionalbecause the dog is so-shaped as-to jam between the opposite surfaces "and 2| when permitted to do so.

The driven member II which is in the nature ofa sprocket 28 is rotatably supported upon a bearing member 30 which is mounted for displacement in respect to shaft '23 and the driving member l0 carried thereby. To the rear of. the bearing member are aflixed cleats 3| and 32, Figs.- 4 and 5, which have guides for engaging the edges 33 and 34, respectively, of a plate 55. vPlate 35 is held in a fixed position by means of a bracket 36 which is amxed thereto by means of bolts 31 and 38. Bracket 35 is, in turn, fastened to the frame of the bicycle by means of screws 39 and 40, Figs. 4, 5 and 6. It is apparent from this construction that the cleats 3| and 32 are adapted to guide the lineal movement of the driven member andsprocket in a vertical direction (Figs. 1, 2 and 5).

In order to displace the driven member H,

and its bearing relative to the driving member and its. shaft 23, a worm 43 and engaging nut 44 areprovided. The worm is mounted upon a shaft 45 which extendsupwardly to the upper cross-bar 45 of the bicycle and is there provided with a crank 41 by which it may be readily rotated. The lower end of the worm shaft is engaged by thrust bearing 48 which is carried by plate 35 and prevents translation of the shaft relative to the plate. Nut 44 is secured to bearing member 30 by means of a pair of bolts 49, 49a, so that the bearing is translated with the nut 44 when the shaft is rotated. The design of the worm and nut are such that the axis of the driven member may be displaced upon either side of the axis-of the driving member. The two axes are shown to the same level, except a slight lustrated in Fig. 2, the axis of the driven member is below that of the driving member. The reason of the slight displacement of the axis of the driven member relative to the axis of the driving member will be explained hereinafter.

To the rear of the drivingmember l0 there is mounted upon a fixed boss 50, a cam 5| which is best shown in Fig. 3. This cam is providedfor determining extremities 'of an arc between whichthe dogs l8 may assume driving engagement with grooves l9. For effecting control of the dogs I 8, .each rocker l5 carries a finger 52 which rides upon the high surface 53 of the-cam 5| during the greater portion of the time that the dogs are disengaged from contact with the opposite surfaces of grooves l9. Inthe construction illustrated in Figs. 1 to '6, inclusive, the cut-away portion 54 of the cam will subtend an are sumciently great to permit freedom of the dog and action of its associated spring for the length of the arc of revolution of the driving member determined by the maximum of the eccentric displacement of the driven member relative to the driving-member. The length of the engaging arc is dependent upon the number of connecting elements provided in any particular mechanism. The driving connection between the driving member and driven member is obtained through the successive action of the connecting elements l2. This is because in positions of eccentricity of the driving and driven" member any particular point upon the driven member. will move at a velocity different from the velocity of any point on the driving member, unless the two particular points are connected together. Accordingly, but i one connecting element l2 and associated dog can function at one time for transmitting motion.

A locked dog causes transmittal of motion to v the driven member through its associated connecting element and, because of the eccentricity of the driving and driven members the dog immediately preceding the locked dog is driven through its connecting arm at a greater velocity ratios of speed transmission are obtained by three a different positions A, B and C of the driving member H in respect to the driven member I. Having reference to Fig.7, A, B and 0' represent three different positions of a connecting element for the three different positions A,

B and C, of the driving member H0 relative to the driven member ill, and A", B" and C" represent three difierent positions of the connecting element for the three different positions A, B and C, respectively, of the driving member H8 in respect to the driven member after the driven member has. been moved through an angle oi; 60, or through the a cuate distance between two successive connecting elements.

Assumingthat the driven member III is to be driven through an arc of 60, the change in ratio' of the driving to the driven members for the difierent positions oi the two members relative to each other, may be understood by' considering the arcs a, and b, which define the limits of the arcs of engagement of the free ends M4 of the connecting elements H2 with the driving member 0 for a 60 rotation of the driven member I. In position A of the driving member, the connecting element will be moved irom the position A to the position A" and its free end 334 will' travel a distance between are a and arc b'equal to twelve teeth upon the periphery of the driving member. In position B of the driving member, the peripheries of the driving member and of the driven member. are concentrio, and the same connecting element will be moved from position B to position'B" and its free end will travel a distance between arcs a and 22 equal to six teeth on the driving member.

With the driving member in position C, the same connecting element will be moved from position Chto position C", and its free end will travel a distance between arcs a and b equal to three teeth upon the periphery of the drivingmemher,

It is apparent that when the axes of rotation oi the driving and driven members are alined end the members are concentric to each other (position 35), thereis a direct drive and a 1 to 1 ratio or the speeds of the two members. This may be expressed as a 6 to 6 ratio and accordingly, the ratio of teeth of the driving member to the driven memberfor the A-position is 12/6 and the ratio of teeth of driving member to the driven member for the C position is 3/6. The

speed ratios are the inverse of the teeth'ratios so that there will be a reduction in speed transmission for the -A position, and increase in speed transmission for the C position, whereas a 1:1 ratio will beobtained for the B position. It is apparent from the foregoing that other positions intermediate the A and -C positions are possible,

and that with 36 teeth on .the driving member, the following diflerent ratios of speed of driving member to driven member are obtainable: 6/12, /9, 6/8, 6/7, 6/6, 6/5, 6/4, 6/3. The number of speed ratios is variable to any degree of limits between the two positions of extreme eccentricity which are permissible in a particular design of any mechanism.

The similar arcs c,- which are markedby a slighter line in the space interposed and immediately exterior to arcs a and b indicate some intermediate positions of the connecting elements on'the periphery of the driving member, a corresponding to an equal number of angular and uniform displacements of the driven member.

It is. evident that, theangular velocity of the drivingmember being kept uniform, when one of the connecting elements'reaches the are a, consequently engaging with the driving member, the velocity of the free end of the connecting element which immediately precedes, and which will have reached the arc b will be gradually in-- creased relative to the peripheric velocity of the adjacent surface of the driving member. Such increasing velocity will cause the connecting element immediately preceding the one which islocked to the driving member to run .forward over the teeth of the driving. member, and con-' sequently to automatically disconnect itself from engagement therewith, so that the said connecting element will be permitted to freely reach the high surfaceof the cam and run over it, as hereinafter described. 1

In order to maintain the ineffective or nonengaging connecting elements out of contact with the driving member, a cam l5l similar to cam 5| illustrated in Figs. 1 to 5, inclusive, is provided. This cam should have a cut-away portion somewhat in excess (if the greatest distance between arcs a and b, in a clockwise direction, Fig. 7, which is at the periphery of drivingmember H0 in position A. The high surface of the cam should extend approximately from the arm b to the are a in a clockwise direction,- Fig. '7, but the cam. should be variable in design, as shown in position B, because while it is necessary to keep the ineffective or non-engaging connecting elements out of contact with the driving member for all eccentric positions of the driving member,

nevertheless when the driving member is in a' concentric position with the driven member all the connectingelements must remain in connection with the driving member, in which case the angular velocity of the two members is the same.

Furthermore, the cam I5l could be variable in design also because it could be desirable to keep all the connecting elements out of contact with the driving member when the ends H4 of the connecting elements are traveling fasterthan adjacent portions of the driven member.

Cam l5! includes two parts H8 and 9 which are pivotally supported upon pins I20 and I24,

respectively. When the axes of the driving and driven members are concentric, the parts H8 and H9 of the cam are disposed entirely within the toothed periphery of the driving member H0, Figs. 7, 17 and 18, and when the a. is of the driving member is eccentric to the axis of the driven member upon either side of the concentric positions of these -members, the two cam parts are separated sufliciently so as to extend beyond the periphery of the teeth upon the driving member.

The manner in which the cam is made variable .for the different positions is illustrated in Figs. 17 and 18. Part H8 is provided with an arm and part H9 likewise is provided with an arm extension I23 extending beyond pivot I2I. The outer ends of these arms are connected by a 2 spring I24 which normally tends to draw arms I22 and I23 toward each other to cause.separation of parts H8 and H9 of the cam. The separated position of the parts H8 .and H9, and hence the expanded condition of the cam, is deitermined by a pair of pins I25 and I26 which engage the arms of a yoke I21 when spring I24 is free to act as, for example, when the cam is.

upon either side of the position for one-.to-one ratio transmission, Figs. 7 and 17. Yoke I21 is carried by fixed bearing member I28 which supwhich supports a bearing for shaft I32 of the driven member or disk I I I.

Yoke I30 has'a pair of arms with fingers I33, I34, diametrically opposite the center of disk III. The distance between the ends of the fingers I33 and I34 is such as to-caus'e the fingers to engage the rollers I35 and I36 carried by the cam when the axes of the driving and driven members H0 and III are co-axial or when there is a one-to-one speed ratio between these two members. Rollers I35 and l36 are so mounted upon parts H9 and 8, respectively, of the cam as to cause the collapse of the cam against the action of spring I24 when the one-toeone speed ratio obtains. axesof the driving and driven members are displaced upon either side of such position, fingers I33 -and'I34 no longer engage the rollers and parts II 8 and II9 of thecam are more distant from each other because of the influence of spring I24. This results in the .disposition ,of the cam beyond the teeth of the driving member III), as illustrated, for example, in positions A and C, Figs. 'Iand 1'7.

In the diagram of Fig. '7, spring II'I continuously urges the free end II4 of the connecting element 2 toward the driving member H0. The free end of the connecting element is provided with a hook for engaging the teeth on the periphery of the driving member. In .the mechanism illustrated in Figs. 1 to 6, inclusive, the counterpart of cam I5I is cam 5I,-and, as clearly seen in Figs. 2 and 3, cam 5| is so shaped as to permit the engagement of the uppermost dog- I8,

and the immediately preceding dog with the opposite surfaces 28, 2I of thegr'ooves I9, whereas the other dogs are, maintained out of contacting relation with the grooves and are held against.

the action of their respective springs II.

This latter condition is accomplishedwhen the fingers 52 carried on pins I6 come into contact with the high surface 5310f the cam (Fig. 3).

.In the mechanism illustrated in Figs. 1 .to 6,-

' elements coming into motion-transmitting function between the driving and the driven mem-I ber can never be in their total number-therefore the mechanism could not operate regularly in the rigorously co-axial position of the axes of-the driving and driven members. It-is in order'to secure the possibility of'a continuous operating their peripheries.

When the 1 particular mechanism as explained hereinbefore.

' well as by tension.

2,028,677 extension In which extends beyond pin I20,

also in the mediate position,as shown in Fig. 1, that it is necessary to keep the two axes slightly displaced in a direction perpendicular to the translating direction, as. indicated by letters '12 and e in Fig. 1, so that such\slight displacement I may allow the succession of the engaging and non-engaging phases of the connecting elements with the driving member-to take place, in virtue of the diiferences of traveling velocity of the adjacent portions, also in the mediate position as illustrated in Fig. 1. i

Also in this'latter case, however, despite the said displacement of the centers in the mediate position, itis obtained that the angular velocities of the driving and driven members are practically l5 uniform and equal to each other.

A structural form of the invention, in which the principles just discussed with reference to Fig-7 are embodied, is illustrated in Figs. 8 and 9. In this construction the driving shaft 60 car- 20 ries two wheels 6|, 62, having hooked teeth upon The connecting elements 63 are pivotally mounted upon a driven member 64 by meansof pins 65. Springs 66 are provided for urging the connecting elements 63 toward the 25 periphery of the driving member. The free end of: each connecting element '63 is provided with a pin 68 adapted to engage the teeth 69. A roller I8, mounted upon each of the pins'68, serves to maintain the pins out of contact with the teeth 3 '69 during the-period of-rotation of the driving member during which the connecting elements 63 are not functioning to transmit motion. The cam which accomplishes this function may be similar to'that illustrated in Fig. 7, or' otherwise 25 designed according tothe requirements of any The clicking eifect which is incident to the over-' running of teeth by a hooked connecting element or pin is obviated in a design in which a locking dog is provided as a part of each connec ng element, as, for example, in the modificatio illustrated in Figs. 11 and 12.

In Fig. 10 I have illustrated a detail ofa modified form of the mechanism illustrated in Figs. 8 4:, and 9. In this form, the driving member 13 is similar to that illustrated in Figs. 8 and 9, but the connecting elements I4 are so designed as to transmit motion to the driven member by com- I pression through the connecting elements. This 50 detail is intended to demonstrate the fact that the connecting elements may be so mounted. and designed as to transmit force by compression as In Figs. 11 and 12 I have illustrated the 55 principal parts of another form of mechanism. In this modification, the driving member 16 car- 'ries a disk 'I'I having a groove {I9 similar to grooves I9 in the embodiment illustrated in Figs. 1 to 6,

inclusive. The driven member consists of a disk co having arcuate- T-shaped slots having centers of curvature correspondingwith the axes of pivot -of the connecting elements I2 (Figs. 1, 2 and 3). Accordingly, the slots 8| will guide. T-blocks 82 in paths corresponding to the paths of travel of the free ends of the connecting elements I2. Each of the blocks 82 carries a pin 83 upon which is mounted a rocker 84 from which a dog 85 extends into the circular groove I9 in the driving member. Each dog 8,5 has an oval or elliptical -70 shape permitting it to slide freely between opposite walls of the groove I9 when the rocker "84 is moved to its extreme clockwise position about its pin83, and which causes it to lock against the f opposite surfaces of the circular groove 19 when the rocker 84 is rocked in a counterclockwise direction about its pivot-83'. The action of the dogs 85 is similar to the action of the dogs l8 (Figs. 1, 2 and 3). reaches the end of a path of travel during which it is locked to the walls of the groove, it will be automatically unlocked because of the varying velocity, as already explained, and its rocking in a clockwise direction about pin 83 will be assured by a cam (such as shown at iii in Figs. 1, 2 and 3) which engages finger 90. This finger is carried by rocker 84.

In Figs. 13, 14 and 15, I have shown still another modification, wherein the driving member 94 is provided with two slightly conical faced disks 95, 96, and the driven member has connects ing elements 9'! which carry at their free ends pivots or rockers 98. Each, rocker 98 carries a pair of rollers 99 through which connection may be had between the disks 95, 96 and the rocker 98. This construction is in the form of an overrunning clutch, and each roller is so mounted as to be capable of being wedged between the none parallel surfaces Hlll, lill upon rocker 98, Fig. 15.. Each rocker is provided with a lug I02, by which the radial position of the rocker about its axis may be controlled. This lug is adapted to be operated by a cam I03 which causes a rising of the rocker and consequently unlocking of the rocker from the disks 95 and 96 by the wedging of the rolls between the non-parallel surfaces I90, IOI. By virtue of the sloping relation of surfaces l00, lill, the rockers will automatically free themselves from locking relation with the disks 95 and 96, as the rockers, at the moment when they come out of engagement, as said before, derive a velocity through the driven member which is greater than the velocity of the driving member at the points ofcontact between the rolls 99 and the-engaging surfaces Hill. The locking of the rockers 98 to the surfaces 95 and 96 by means of the rolls 99 is caused by the action of springs disposed similarly to the springs I ll indicated in Fig. 7, acting upon the connectingelements 97. I

The diiferent forms of the invention illustrated in Figs. 7 to 15, inclusive, are for the purpose of showing different modes of applying the principle of my invention, and no attempt has been made to illustrate complete details of the various elements. The different examples have been given for the purpose of illustrating different modes of applying the principle of the invention which is more carefully explained in reference to the construction illustrated in Figs. 1 to 6, inclusive, and by the schematic showing in Fig. 7.

What is claimed is:

1. In combination, a variable speed transmission mechanism, comprising a pair of members including a driving member and a driven member mounted for rotation and translation in respect to each other, means for guiding one of said members in translation in respect to the other member in a line to one side of the center of rotation of said other member and extending to opposite sides of their positions for one-to-one When a particular dog.

ing and driven members. A

ratio of transmission, and means including connecting elements for connecting said two members together so as to cause continuous motion transmission in all the relative positions oi. the, axes of rotation of the members, the guiding by 5 said guiding means of one of said members in a line to one side of the center of rotation of the other of said members resulting in enabling variation in the ratio of transmission through a one-to-one ratio from a high speed to a' reduction speed, depending upon the relative positions of the axes of rotation of the driving and driven members, without interrupting the continuity of motion transmission.

2. In combination, a variable speed transmission mechanism, comprising a driving member and a driven member mounted iora-otation and translation in respect to each other, means for supporting said members in different relative poof the two members on oppositesides of their positions of one-to-one ratio of transmission and displaced from one another normal to their axes for a one-to-one ratio of transmission, means including connecting elements for connecting said two members together so as to cause continuous motion transmission in all the relative positions of the axes of rotation of the members, and means for controlling the are through which said connecting elements automatically comeinto effect for producing a driving connection between the driving member and the driven member in different relative positions of said members.

3. In combination, a speed transmission mechanism for use between a driving shaft and a driven 35 shaft having a variable eccentricity relative to one another, driving and driven members. mounted respectively on said shafts and having force transmitting elements carried by said members and entering into and coming out of engagement 40 J for causing connectionand disconnection between said members, depending on whether or not said elements are overrunning, variable cam means for guiding said elements when overrunning, and means for collapsing said cam means for allow 45 ing contemporaneous engagement of .all of the force transmitting elements when the driving and driven members are substantially coaxial- 4. In combination, a speed transmission mechanism for use between a driving shaft and a driven 50 I shaft having a variable eccentricity relative to oneanother, said shafts also being eccentric to each other in a direction normal to the direction of said variable eccentricity, driving and driven members mounted respectively on said 55 shafts and having force transmitting elements carried by said membersv and entering into and coming out of engagement for causing connection and disconnection between said members, de. pending on whether or not said elements are overno running, and cam means for guiding such of said force transmitting elements which are overrunning and not serving to connect together the driv- 05 ALVARO VINCENZONI. 

